Automatic lathe



- Oct. 29, 1946.

w. F. GROENE ETAL AUTOMATIC LATHE Filed Feb. 10, 1943 11 Sheets-Sheet l INVENTORS. W\LL\F\M F. GROENE MP. Eh d PP. $w\ 0 mm! 3/ r3. o5 m$ R K H HIE ATTORNEY 06L 1946- w. F. GRQENE ETAL ,0

AUTOMATIC LATHE Filed Feb. 10, 1943 '11 Sheets-Sheet 2 E INVENTORS.

' MLUAM F. GRGENE BY m RY cxemr k ATTORNEY.

1946- w. F. GROENE |-:'r AL ,0

AUTOMATIC LATHE Filed Feb. 10, 1943 ll Sheets-Sheet 3 WILLIAM F. GROENE BY i HARRY C.KEMPER Oct 1946. w. F. GROENE ET AL 2,410,026

AUTOMATIC LATHE Filed Feb. 10, 1945 I 11 Sheets-Sheet 4 INVENTORS. WlLLlAMEGROENE BY HARRY C..KEMPER NT'YORHEY.

06L 1946- w. F. GROENE ET AL 2,410,026

AUTOMATI C LATHE Filed Feb. 10, 1945 ll Sheets-Sheet 5 INVENTORS.

' MTDRNEY.

wlLum EGROEHE may 0. KEMPER 6- T w. F. GROENE ETAL 2,410,026

AUTOMATIC LATHE Filed Feb. 10, 1943 r 11 Sheets-Sheet e WILL-MM F. GROENE Oct 29, 1946- w. F. GROENE ET AL 2,410,025

AUTOMATIC LATHE Filed Feb. 10, 1943 ll Sheets-Sheet 7 151 Y E BY HARRY C.\ EMFER AT TORNEY" Get 29, 1946.

w. F. GROENE ET AL AUTOMATIC LATHE Filed Feb. 10, 1943 11 Sheets-Sheet 8 INVENTORS. WILLIAM F. GROIENE umzrq c. KEMPER AT T ORNEY..

Oct 29, 1945- w. F. GROENE ET AL 2,410,025

AUTOMATIC LATHE Filed Feb. 10, 1943 11 Sheets-Sheet r9 INVENTORS. MHLLIAM F. GROENE HARRY C.KEMPER' ATTORNEY.

Oct. 29, 1946 W.F 'GROENE ETAL 2,410,026

' AUTOMATIC LATHE Filed Feb. 10, i943 11 Sheets-Sheet 10 Pram" 1NVENTOR5- wmum F. GROENE BY ARRY c. KEMPER mm 3 M ATTORNEY.

946. W..F. GROENE ET AL 2,410,026

AUTOMATIC LATHE Filed Feb. 10, 1945 ll Sheets-Sheet ll 1ss-b 4 INVENTORS. egg 522x59: FE 21H BY 99 I .g

ATTORNEMY.

Patented Oct. 29, '1 946 AUTOMATIC LATHE William F. Groene, Cincinnati, and Harry G. Kemper, Goshen Township, Clermont County, Ohio, assignors to The R. K. Le Blond Machine Tool Company, Cincinnati, Ohio, a corporation of Delaware Application February 10, 1943, Serial No. 475,342

2 Claims.

This invention pertains to automatic lathes and is particularly related to the transmission and control mechanism for such type of lathes. Primarily the purpose of this invention is to provide an automatic lathe of completely universal charin the lathe.

It is also a further object to provide, in conjunction with this feed and rapid traverse mechanism, a load-and-fire trip mechanism for alternately engaging the feed and rapid traverse motion at the appropriate time in the cutting cycle of the machine; 1

Another important featureof this invention is to provide aseries of tool carrying bars upon which are mounted the tool holders or slides carrying the cutting tools so that one bar extending longitudinally of the lathe spindle axis is located directly below said spindle axis for carrying the turning tools. The second bar is also provided immediately under and directly below the work spindle andfirst mentioned bar for carrying the facing tools. The result of this unique arrangement is to provide much greater clearance room for the chips cut from the work piece in the lathe and at the same time provide much greater accessibility to both the work and tools of the machine A further object is to provide in this arrangement of .tool bars extending longitudinal of the .axis of the lathe, one above the other with the 1 upper bar mounting the turning tool and the lower ,b'ar directly beneath it mounting the facing too1 ;feeding devices, means whereby either the front ,or rear tools may be alternately or simultaneiously utilized for either turning or facing opera- :tions.

Further features and advantages of this invention will appear from the detailed description ,of the drawings in which:

Figure I is a front elevation of the automatic lathe of this invention showing the general arrangement of the base, headstock, tailstock, and overhead too1 slide.

Figure II is a rear elevation of the automatic lathe shown in Figure I.

Figure III is a left hand end elevation of the lathe shown in Figures I and II. i

Figure IV is an enlarged fragmentary view partly in section of the headstock, control mechanism, and feed cams for the tool slides shown on the line IV-IV of Figures V and VI.

Figure V is an enlarged fragmentary transverse section through the lathe headstock and bed on the line V-V of Figures 1, IV, and VII, particularly showing the belt drive transmission to the work spindle and the spindle stop trip mechanism.

Figure VI is an enlarged fragmentary transverse section through the lathe headstock on the line VI-VI of Figures IV and VII, particularly showing the feed and rapid traverse drive and control mechanism. i

Figure VII is a diagrammatic section through the transmission mechanism of the lathe headstock, particularly showing the headstock jdriving transmission comprising the gear drive and belt drive mechanism for rotating the work spindle together with the power takeoff mechanism for the feed and rapid traverse movement to the tool slide, shown on the line VII-VII of Figures V and VI.

Figure VIII is an enlarged transverse sectional view through the lathe, on the line VIII-VIII of Figures I and II, particularly showing the facing tool on the lower tool bar and the turning tools on the upper tool bar of the lathe, together with the cam actuating mechanism for feeding said tools relative to the work spindle, the tailstock for the lathe being shown in the background.

Figure IX is a fragmentary enlarged rear elevation of the universal tool slide'mounted on the overhead tool barishown by the line IXIX in Figures III, XI, and XII, particularly illustrating the cam actuating mechanism having the constant feed to depth and dwell position for any position of adjustment of rate of feed.

Figure X is an enlarged fragmentary front elevation of the universal tool'slide on the overhead too1 carrier shown by the line X--X in Figures III, XI, and XII.

Figure X1 is a left hand end elevation partly XIII-XIII of Figures II and IV, particularly showing the feed and rapid traverse clutch shaft. Figure XIV is an enlarged detail view of the cam controlling the rate of feed and dwell for the various cutting tool slides.

Figure XV is a view of the pinion shaft for setting the cam slides.

The lathe comprises a base "I upon which .is

rigidly [mounted a headstock 2 and the tailstock 3. The work is held in the lathe n the centers 4 and 5 carried respectively in the headstock work spindle 3 and the tailstock barrel 1.

Referring particularly to Figures III and VII the work spindle 6 which carries a suitable chucking device or work arbor for driving the work in addition to the center is driven from the main drive motor 8 which is connected through suitable belts 9 to the clutch and brake pulley 10 which incorporates a driving clutch l l and brake device l2 which may be actuated by reciprocating the actuating rod I3 by moving the spool M which engages the actuating fingers I5 in a conventional manner, for example, as shown in Patent #1,474,-112,-dated November 13, 1923 Thus main drive power from the motor =8 and the pulley It) may be connected to the input drive shaft l6 through the friction clutch H or may be disconnected from the shaft Is by this clutch and the shaft I6 and associated headstock transmission gearingstop-ped rapidly by means of the brake l2.

On :the shaft 16 is fixed the gear I! which is arranged in driving relationship with the gear 48 fixed on the shaft l9 appropriately jo-urnaled in the headstock housing '2. The outer right hand end-of the shaft [9 extends into a change gear compartment 29 and 'has mounted on it a gear 2| which may drive the pulley shaft 22 when a changegear 23 is inserted on the outer end of this shaft 22 which meshes with the gear 2-! on the shaft 49. Or thegear 23 may beremoved and placed on theshaft .24 .so that driving ower 'from'th'eshaft .l 9 .may then be transmitted from the gear :21 to the gear 23 on shaft 24 to effect the'geardrive to the work spindle.

When belt driving of the lathe spindle 6 is to be done, :the gear :23 is placed on the shaft 22 whereby driving power from the main drive motor 8 is transmitted to this shaft and to its pulley 25 which is connected through the belts '26 to a pulley 21 fixed to the work spindle 6 and which belts may be kept in proper tension, Figure V, by means of the eccentric idler adjusting means comprising a pulley 28 mounted on suitable bearings 29 and carried on an eccentric bushing 30 fixedtoan actuating stud 3i which'has a squared end portion 3.2 for application of a wrench for rotating the stud ,3I to effect adjustment and tension in the belts '26. A suitable lock nut 33 is provided for locking the stud :3! in the desired P Q Q A- When gear driving of the work spindle 9 is to be undertaken, gear 23 is placed on the end of the shaft 24 in the compartment 29 whereby the shaft 24 is. rotated and the double gear 34fixed thereon and having the gear portions 35 and 3.9 will thus bedriven. The gear 35 may be engaged by'the gear 31 when the shiftable gear comprising the gears 31 and 38 is moved to the left on the shaft 39 while at'the same time when gears 35 and 31 are in engagement the gear 31 also engages the gear 40 fixed on the work spindle 6. When the gear 3738 is shifted to the right on the shaft 39 the gear 38 engages the large face gear 4| fixed on the work spindle 6. In this way two changes of gear drivespeeds may be effected in the work spindle 6. Thus by this arrangement the work spindle may be driven directly by belts for the higher smoother speeds required or a gear drive having two selections of speed may also be obtained when the gear 3'f38 is shifted to the position where gear 31 engages gear 35 of shaft 124 and gear 40 of the work spindle, or when its gear 31 engages the gear 36 of the shaft 24 and its gear .38, engages the face gear 4| on the work spindle.

In this transmission arrangement it Will be noted that there are two compartments in the lathe headstock, namely the lubricant filled compartment 42 which provides lubricant for the gear transmission mechanism and the dryicompartment 43 which contains no lubricant and contains the belt drive transmission as shown best in Figures V and VII. A suitable lubricant tight bafiie 44, Figure V, is provided in the bottom of the dry compartment 43 so as to prevent any lubricant getting into the belt drive transmission and impairing its efficiency. Another unique feature of this design lies in the fact that the work spindle 6 need not be removed from its journal bearings 45 and 49 when it becomes necessary to replace the belts '26. This is accomplished by providing the rear mounting bearing 4'! of the work spindle in a cartridge case 48 which may be entered into a bore 49 in the headstock housing 2 and held in place by suitable screws 59. When it is desired to change the belts zfithescrews 50 are removed and the cartridge case 48 and the lock nut 5| removed from the work spindle. The clearance thus provided between the bore 49 and the work spindle is just sufficient to permit easy removal or insertion of the belts through this opening and around the work spindle 6 so that they may then be easily slipped over the pulley 25 and the idler pulley 28. The cartridge case 48 is then reinserted in the bore 49 and fastened in placeby the screws 50 to thus provide a totally enclosed integral headstock containing a lubricant filled gear drive transmission compartment and a dry belt drive compartment in the same head housing. This arrangement, of course, provides the utmost simplicity and efficiency in manufacturing of a lathe headstock incorporating such features.

Power for actuating the cutting tools at feed and rapid traverse motion is derived from the headstock transmission. Referring particularly to Figure VII, on the shaft i9 is fixed a gear 52 which drives the gear 53 rotatably journaled on the shaft I ,6 and which has formed on a sleeve projecting portion thereof a spiral gear 54 and a second spiral gear 55 fixed to the other end of the sleeve of the gear 53. The spiral gear 55 drives a mating spiral gear 59 carried on a shaft 51 appropriately journaled in the headstock housing ,2. "This shaft '51 proceeds backwardly .to the rear of the headstockinto a change gear compartment 58, Figures II and where it has mounted on it a change gear 59 which meshes with another change gear 6.9 in this same compartment '58 mounted on the shaft .61 appropriately journaled in the lower rearward portion of the headstock housing 2, Also on this shaft journaled against axial movement is the spiral gear 62 which meshes with the spiral gear 54of the gear 53 above mentioned. Thus by this arrangement the shaft 6| may be driven at a plurality of diiferent relatively slow speeds or feeding speeds by changing the change gears 59 and 69 in the compartment 58 for effecting different rates of relative feed for the tools of the machine. The spiral gear 62 rotatably mounted on the shaft 6I is driven at a relatively rapid rate by its mating spiral gear 64 so as to efiect rapid traverse motion. In order to selectively take off either the feed drive power from the shaft 6| or rapid traverse driving power from the spiral gear 62 the ar rangement shown in Figures VI and-XIII i provided which comprises a clutch member 63 fixed by suitable pins '64 to the shaft M and having clutch teeth 65 which are arranged to engage mating clutch teeth 66 of the output gear 61. This output gear 6'! is journaled on the shaft BI and has clutch teeth 68 which are arranged'to engage clutch teeth 69 formed on the gear 62. Thus by shifting the gear 61 so as to engage the clutch teeth 66 with the teeth 66 of the clutch member 63 this gear 6! will be rotated at feeding speed. Shifting this gear 61 to the left, Figure VI, will engage the clutch teeth 69 with the clutch teeth 69 of the gear 62 so as to connect rapid traverse power for rapidly rotating the gear 61. This gear 61 is in constant mesh for any shifted position with the idler gear 19 appropriately journaled on a suitable stud 19a in the headstock housing 2. This gear I9 may be connected to or disconnected from driving relationship With the worm shaft II by means of a pinion I2 slidably but drivably mounted on the shaft II by any suitable splined connection and may be slid on this splined arrangement by means of the control rod I3 having an operating knob I4 projecting through the front of the base I of the lathe as best seen in Figure VI. This worm shaft .II has fixed on it a worm I6 which in turn drives a worm wheel I6 fixed on the cam drum shaft 11 appropriately journaled in suitable bearings I8 and I9 in the base Iof the machine, A suitable crank handle not shown may be placed on the clutch portion 89 of the worm shaft when the knob I9 is pushed in against the base I of the machine as shown in Figure VI so as to rotate the shaft II manually for effecting manual positioning of the tools for setting the work and tools prior to the automatic machining cycle. On the cam drum shaft II are appropriately mounted the cam drums SI and 82 having appropriate cam slots 84 and 85 for actuating the various tool slides in their desired movement.

Referring particularly to Figures IV, VI, and VII, the control of the clutch II on the input drive shaft I6 is accomplished by means of the main spindle stop and start lever 66 which is fixed to an appropriate sleeve 91 journaled in the headstock housing 2 and having fixed on its inner end a depending lever 88 which is connected by means of a link 89 with another lever 99, Figure V, pivotally mounted on a pin 9I fixed in the headstock housing 2 and having a yoked portion 93 carrying a shoe 94 which might be fitted in the annular groove 95 of the operating spool I4, Figure VII, of the clutch II. Thus by moving the lever from its position 86a, Figure IV, to the position 861) the clutch spool I4 will be moved to the left in Figure VII to engage the clutch II; likewise moving the lever in the opposite direction will disengage the clutch I I and engage the brake I21 for rapidly bringing the work spindle 6 to a stop.

This operating handle and clutch' II may be automatically tripped to stop the spindle at a predetermined point in the work cycle from the rotation of the cam drum shaft 'I'I asfollows: Noting Figure V, on the pin 9| and in the cutaway portion formed in the lever 99 is mounted the lever 96 which has an upward projecting lug 91 having a surface 98 engaging the surface 99 of the lever piece 99 but which is free to rotate, as seen in Figure IV, in a counterclockwise direction without effecting rotation of the lever 99. Rocking the lever 96 clockwise actuates the lever 99 and therefore the control lever 86 to the stop and brake positionof the clutch I II2. A suitable compression spring I99 carried on an eyebolt I9I and abutting against the nut I92 engaging the surface I93 of the headstock housing 2 and is connected by means of the pin I94 to the lower end of the lever 96 so as to normally urge this lever 96 in the clockwise or stop and clutch disengaging position. Also on the lower end of this lever 96 is a latch piece I95 which is adapted to be engaged by a mating latch piece I96 fixed on a lever I9! fixed on the rock shaft I98 journaled in the headstock housing 2. Also fixed on the left hand end of this rock shaft I98, Figure IV, is the roller arm I99 carrying a roller III] which may be engaged by a dog I I I appropriately clamped by a suitable screw II2 on the shaft I1. Normally this arm I99 and lever I91 are moved so as to constantly be urged toward the latch piece I95 of lever 96 so that when the lever 86 is moved to the position 8619 compressing the spring I99 it will automatically be latched by the piece I95 engaging about the piece I96 so as to hold this lever in the run position for the work spindle. As the cam drum thus rotates through the transmission gearing to the worm I6 on the shaft H as already described the dog III will rotate around and ultimately strike the roller II9 on the lever I99 at the appropriate time in the cutting cycle as determined by the setting of the dog III by means of its adjusting screw II2 on the shaft TI. Thus when the dog I I I does hit the roller III! the spindle stop lever will be tripped to the stop position since the member I96 will be pulled away from the member I95 by this actuation of the lever I99 allowing the spring I99 to turn the lever 86 to the stop position 9611. It will be also noted that since the surface 98 engages the surface 99 of the lever 99 only from the clockwise direction of movement that even though the lever 96 is latched behind the latch piece I96 of lever I9I during the automatic cycle the stop lever 86 could at any time be moved back from position 8% to 86a manually to immediately arrest the work spindle rotation in the event of an accident or any other incorrect operationof the machine.

The gears 3"I38 on the shaft 39 may be shifted axially on this shaft for effecting the two ranges of gear driving of the work spindle 6 by means of-the control lever II3 located on the front of the headstock as shown in Figure IV. This lever H3 is fixed on the rock shaft II4 which passes co-axially through the sleeve 8'! of the lever 86 and has on its inner end a shifter lever I I5 carrying a shifter shoe I I6 which engages in the annular groove II1 formed in this gear 3'I-38, so that rocking of the lever from the position 341 to the position II 3b effects shifting of the gear to its true driving position as described above.

Feed and rapid traverse power may be alternately applied to the cutting tool of the lathe automatically at a predetermined position of the cutting cycle of the machine. Thisautomatic 7 control of the feed and rapid traverse movement is effected from the rotation of the cam drum shaft 'I'I. Referring particularly to Figures IV, V, and VI it will be noted that the clutch gear 61, Figure VI, has an annular groove I I8 in which is mounted a shoe I I9 which is carried by a yoke I20 fixed to the rock shaft IZI journaled in the headstock 2 of the lathe. On this rock shaft I2I is mounted a downwardly depending link I22 which has a projecting pin I 23 which may be engaged by the screws I24 and I25 of the fork .shaped lever I26 fixed on the rock shaft I2I journaled in the headstock housing 2. This rock shaft I2! proceeds to the left, Figure IV, and has fixed on its outer end a pair of levers I28 and I29 each with rollers I33 and I 3I respectively. The arm I28 having the roller I39 is engaged and roperated so as to rotate the rock shaft I21 in a clockwise direction by the trip dog I32 while the lever I29 has its roller I3I engaged by trip dog I 33 which rotates the rock shaft I2! in a counterclockwise direction, as seen in Figure V. Both of these dogs I 32 and I33 are respectively clamped at their desired circumferentially oriented position on the cam drum shaft IT by suitable clamping screws I34 and I35 respectively. It will thus be seen that as the cam. drum shaft 'I'I rotates the dog I32 will strike the roller I30 so as to cause the rapid traverse motion to take place by engaging the clutch teeth 58-459 whereas the shifter I33 when it engages the roller I3I and lever I29 the feed clutch 6566 will be engaged to effect the feeding motion in the cam drum shaft and tool slide of the lathe.

In order that the transition from feed to rapid traverse or from rapid traverse to feed may take place by snap action motion so that at no time shall the cam drum shaft ll get to a neutral position and therefore stop the entire operation of the machine, a special arrangement is provided for flipping the clutch gear 61 from one position to the other. This comprises leaving a substantial space for lost motion between the shoe III! and the annular slot H8 in the gear 61 and in providing a lever arm I36 having a pin I3'I which is carried fixedly to the shaft I2I so as to rock or swing with the motion of the shaft I2I. A detent lever I38 having a detent point I39 and pivotally mounted about the shaft I2! is normally urged into yieldable position against the pin I3! by means of the tension spring I44] attached to the lever I38 and to a pin I II fixed in the headstock housing 2. The point I39 of the detent lever I38 is so arranged that as the shaft I2I is rocked to cause disengagement of the clutch gear 61 with either of its respective clutches, that the lost motion between the shoe I I9 and the slot I I3 permits the pin I 31 to ride a little beyond the point I39 in the direction it is moving so that just as the shoe II9 begins topengage the other side of the slot III3 for removing or disengaging the clutch the remainder of the motion will take place due to the sliding of the pin I31 down the surfaces I42 or I43 each side of the point I39 in a snap action fashion so that the clutch will then be moved immediately to disengage one clutch or immediately engages .the other series of clutches so that at no time is there a position where the clutch gear 61 is in a neutral or no clutch engaged position. This is essential in order that the cam drums on the shaft 1-! at all times be rotating in either rapid traverse or feed so that the trip dogs III, I33, and I32 may at all times be moved to effect control of the levers I09, I29, and I 23, The said screw I24 and I25 in the lever I26 are primarily for the purpose of accurately positioning the various levers I28 and I29 with respect to the clutch gear 61 so as to provide the proper degree of accuracy of movement of all of these members during the automatic operating cycle of the machine.

Referring particularly to Figures I and VIII it will benoted that extending longitudinally of the base of the lathe is the upper tool supporting bar I44 and the lower tool supporting bar I45 both located with their axes substantially in a vertical plane passing through the work spindle axis I46 of the lathe. In this particular exemplary disclosure the'bar I44 is journaled for sliding and rocking motion in appropriate bearings I47 and I48 in the base I of the lathe as best shown in Figure VII and is similarly supported in appropriate bearings I49 in the tailstock 3. The lower tool bar I45 is supported in bearings I50 and I5I in the base I of the lathe and is permitted to rotate in, said bearings but is restricted from axial sliding motion in this particular instance v by appropriate collars I52 and I53 clamped to the bar I45. It will be noted that this arrangement of the bars I44 and I45 one above the other and lying substantially in a vertical plane passing through the axis of rotation of the work spindle that there is no obstruction on either side of this central vertical grouping of the bars I44 and I45 so that chips cut from the work piece mounted on the work spindle axis have free access to drop down past these bars into a relatively wide chip collecting compartment in the base I comprising the vertical longitudinally extending rear portions Ia and Ib forming the compartment I c through which the chips readily drop into the pan I54 below the base I of the machine. Also since there are no obstructions from these bars far removed from the vertical plane passing through the axis of the Work spindle, the operator is not. interfered with in reaching to the tools and working from either side of the machine to thus make apractical machine operation in a line-up where one operator would operate a plurality of. machines and be required to operate the machine from either side. Also adequate chip space is thus provided which is a very important feature of a lathe of this automatic type whichproduces chips at a very rapid rate during its rapid production of work pieces.

The upper bar I44, while free to rotate, is also given axial sliding motion by means of the actuating block I55, shown best in Figures VI and VII, which has a slotted portion I56 in which nicely fits a collar I 51 fixed on the bar I44 by a suitable pin I58 so as to permit the bar I 44 to rotate in the bearings I41 and I48 of the headstock and also in the tailstock bearings. In this way the block I accurately controls the axial movement of the bar I 44. The actuating block I 55 has a bore I59 which nicely fits over the lower bar I45 and slides thereon so as to support the block I55 against swinging about the bar I44. On the lower end of this block I55 is a cam roller I50 carried on a pin IBI fixed in the block I55 and which roller I39 may engage in a cam track 84 on the cam drum 8I so that rotation of the drum BI on the shaft 11, through the mechanism described, will cause axial displacement of the member I55 along the lower bar I45 and to thus cause axial motion in the upper bar I44 through the medium of the collar I51.

Extending longitudinally of the base I and par-' allel with the work spindle axis of the lathe is the actuating cam slide- I62 carried in suitable guide way surfaces I64 and I65, and on the anti-friction supporting rollers I66 in the Web member Ia of the base I and the cam slide I63 is carried in guide ways I61, I68, and on the supporting rollers I69 in the web portion lb of the base I of the machine in this particular arrangement the turning tools or tools which feed substantially parallel to the axis of rotation I46 of the work spindle are mounted on the upper tool bar I44 and comprise a tool slide base I 19 which may be clamped to the bar I44 by means of a clamping screw I1! and which has mounted on top of it a tool slide or holder I12 having an adjustable screw I13 for accurately moving it to set the cutting tools I14 in the tool block I 15 to proper depth and accuracy of out. On this tool slide base I19 is pivotally mounted on a pin I16 an abutment finger I11 which engages the top surface I18 of the form bar I19. The form bar or plate may be clamped to the Vertical cam plate I89 carried between guide rollers I9I in a bracket I82 fixed to the base I of the machine by suitable screws I83. By suitable bolts I84 passing through clearance holes I85 the form bar I19 is held on the cam plate and may be set at any desired adjusted position ofeither parallel or taper turning by means of the adjusting screws and nuts I86. The cam plate I89 has a suitable cam engaging roller pin I81 carried on a suitable anti-friction ball bearing I88 for easy rotation when bearing against the cam surfaces. This roller pin I81 engages in a slot I89 formed in an adjustable cam I99 Which is pivotally mounted around a T-slot bolt I 9! held in a T-slot I92 formed in the cam slide I63 so that it may be swung around this T-slot bolt I9I to effect different angular positions of adjustment such as shown in Figure XIV indicated at the I892; position of adjustment of the cam slot for a minimum of angularity to the cam while the position I99 shows the steepest position. At the other end of the cam I99 is out a rack I93 whose arcuate shape is radially positioned from the axis of pivoting of the cam around the T-slot bolt I9I. bore I94 is formed in the end of the slide I63 for insertion of a pinion gear I95 carried on a shaft I96 (Figure XV) having an operatingknob I91 for easy positioning of the cam I 99 to the desired angular setting. A clamp I99 operated by a suitable bolt I 99 and having a lipped portion 299 may be tightened to lock the cam I99 in any desired angular position of setting, after which the bolt I9I is similarly tightened to rigidly hold the cam for operating the machine.

Referring particularly to Figure XIV, it will be noted that the portion of the cam embraced by the angle 29I is radially positioned with respect to the point of pivoting around the bolt I9I and this portion of the cam is so arranged as to give the proper dwell and accurate positioning of the tools to the work and by means of this constant radial positioning of the angular portion 29I of the cam slot I89 the cam may be set to any de sired angular position of feeding while at the same time always maintaining the same dwell or finish position of the tools. When readjusting the cam to any desired position of setting along the T-slot I92 of the cam slide I63 it may be desirable in some instances to withdraw the engaging roller stud I81 which may readily be done by removing the screws 292 and pulling out the carrying cartridge on the stud 293 by means of its manipulating handled portion 294 as best seen in Figure VIII.

1 This front cam slide I63 has fixed on it a roller 295 carried on a stud 296 fixed in the cam slide A suitable which engages a cam slot 84 of the cam drum 8I so that rotation of this cam drum 9i causes sliding motion in the cam slide I63 which also carries the cam I99 which thereby actuates the stud I81 to cause vertical sliding movement in the cam plate I89 and through the medium of the form bar I19 bearing against the abutment block I11 to swing the tool holder in the arcuate path of feeding 291, Figure VIII, to present the tools I14 to or from the work. This motion may be utilized either as performing facing operations with the tools I14 or the cam drum 8| may be so arranged as to effect motion sufficient to merely cause the tool relief in the turning tools I14 from the work during their longitudinal return movement.

Turning motion for the tools I14, that is the longitudinal or parallel feeding of the tools with respect to the work spindle axis I46 is accomplished as above described by longitudinally or axially sliding the bar I44 to which the tool slide base I19 has been rigidly clamped by the screw I1I through the medium of the block I55 also operating on the cam drum 8I. Thus in this particular exemplary arrangement it is possible to have facing or radial infeeding of the tools I14 with respect to the tool spindle axis or to have longitudinal feeding of the tools alongsaid axis. Also in instances where pure turning is to be done the tools I14 are moved parallel to the work spindle axis by axially sliding the bar I44 and arranging the surface I18 of the form bar I19 in parallel relationship to the work spindle axis and by so arranging the cam I99 that it will have no motion effecting the vertical movement of the cam plate I89 during the normal turning operations. This cam I99 however would in this instance have certain relief portions out in it where the cam plate I89 would drop down slightly just after the completion of the turning operation on the work so as to relieve the tools therefrom, during the return movement of the bar I44 in bringing the tools I14 to initial cutting position.

It is also to be noted that taper turning can be readily done with this construction by merely setting the form bar I19 in angular relationship to the work spindle axis in proportion to the desired taper to be cut on the work piece. Pure facing operations would be accomplished with 50 the front tools I14 by merely having the cam plate I99 fully operative to effect vertical move- -ment in the cam plate I99 during which time the bar I44 would be locked against axial motion and would have only rocking motion for the 55 tools I14.

In this disclosure also is shown a similar setup for actuating the facing tools which are carried on the bar I45 by means of the facing tool holder 291 which may be clamped to the lower 69 tool bar I45 by a suitable clamping screw 298 and which has mounted on it a tool block 299 carrying the facing tools 2I9. Similarly this facing tool holder 291 has an abutment block 2| I mounted on a suitable pivot pin 2I2 which engages the form bar 2I3 which is similarly held into place by screws 2I4 on the cam. plate 2I5 and which may be adjusted in the desired position by the adjusting screws 2I6, in a fashion similar to that for the arrangement for actuat- 70 ing the cutting tools I14. In this instance however the abutment block 2 II is carried on an adjustable piece 2I1 which may be locked in varioust positions in the arcuate guideway 2I8 by means of the clamping bolt 2I9. In this way a greater range of relative positioning of the tools I ll 2I0 with respect to the work spindle axis may be effected along its arcuate path of feeding 222. The cam slide I62 similarly carries a cam 22! like the cam I9!) just described for the front tool slide turning tool I14 which actuates a roller pin 222 carried in a suitable anti-friction bearing 223 in the cartridge 224 held in place by screws 225 on the vertically movable cam plate 2I5. This cam slide I52 similarly has a roller like that of the cam slide I63 indicated at 225 carried on a'stud 221 (Figure VI) which engages in a suitable cam track 84 in the cam drum 8!. In this instance of utilizing the rear tool holder 221 on the bar I45 primarily for facing or radial infeeding of the tools 2Iil along the arcuate path of feeding 220, bar I45 is confined against axial movement by the collars I52 and I53 and that purely vertical motion in the cam plate 2!?! effected through the medium of the roller pin 222 and movement of the cam slide I52 by the cam drum 8! is utilized. It is to be further noted that in this particular arrangement because of utilizing the lower bar M for racing rather than the front bar, that lesser arcuate path of feed 2253 is provided and a greater range of facing may thus be undertaken. By maintaining the bars I44 and I45 substantially in the same vertical plane passing through the work spindle axis the chips are easily disposed of asthey dropfreely into the pan of the lathe and also easy accessto the cutting tools is thus provided from either side of the machine.

The cam drum 3! is designed with appropriate cam slots (not here shown in detail as this mechanism is readily understood and well known in the art) for actuating the block I55 and the cam slides I53 and I52 in appropriate sequential relationship to effect the various operations de: sired of the lathe of both tool reliefs and feed motion either radially into the work for facing or longitudinally of the work for turning.

In addition to the cutting tools II I and 2!..3 just described there may be provided additional tooling comprising the cutting tools 228, Figures I, XI, and XII carried in appropriate tool block 229 mounted on a vertical universally mounted tool slide 23% This tool slide 232 is mounte-d on suitable dovetail guideways 23! and 232 on a base 233 which is mounted on a swivel around the axis of an actuating shaft 232 appropriately journaled in the supporting housing 235' to which the base plate 235 is fixed by means of suitable T-slot bolts 231 operating in a concentric annular T-slot 233 formed in the base plate 236. This base plate 235 in turn is mounted to the overhead tool supporting rail 23% by suitable T-slot bolts 246, as best seen in Figure XI. In this way the tool slide base 233 may be set to any desired angular position so that the cutting tool 228 may be fed at relatively steep angles for cutting such work as bevel gear blanks and the like.

This overhead tool supporting rail 239 is mounted on the headstock by suitable means such as the bolts 24! and is carried on a pedestal 242 appropriately mounted on the tailstock by screws 243 and connected to the overhead rail by screws 244. In this overhead tool supporting rail 239 and guided in the guideway 245 as best seen in Figures II and IX is the cam slide'245 which carriesv an actuating cam 24'! of similar design to that of the cams I93 and 22!, Figure VIII,

already described. This cam may similarly be adjusted by manipulating the clamp bolt 249 and its clamp 25!] for setting the desired rate of 7 the end of the base I of th machine.

feed for the cutting tool 228. This cam 241 has a cam slot 25! which actuates a pin 252 fixed in a slide plat 253 having a rack 254 formed integral with it which rack in turn is in engagement with a pinion 255 carried on the actuating shaft 234 and which may be connected to it in driving relationship through the medium of the hub 255 to which it is integrally connected when the setting screws 251 of the orienting coupling 258 are properly clamped. The outside portion 259 of the coupling 258 can be positively attached to the actuating shaft 234. The purpose of this coupling 258 is to permit the proper orientation of the pinion and rack with relationship to the cam for starting the tool at the right end of the desired position for beginning the cutting operation. I

On the other end of the actuating shaft 234 is fixed a pinion 25E] Figures X and XI which drives a mating pinion 25! carried on a suitable stud v2I52 fixed in the base plat 233 and driving a rack 253 fixed on the tool slide 23! compression spring 234 is used to normally force the tool slide away from the work piece to at all times take out any slack between the rack and pinion and cam driving mechanism just described during the turning operation and to prevent the tool slide 235 and the tools 228 from dropping down toward the work piece when cutting action is relieved therefrom and which would otherwise make it difficult to do accurate finishing with this cutting tool. This is accomplished by spring 264, engaging in the upper portion 255 of a suitable bore 266 formed in the slide 233 and bearing against a guide block 261 rigidly fixed to the base plate 232 by suitable screws 268. It can thus be seen that as the cam slide 246 is moved'back or forth in the guideways 245 its cam actuating means and roller pin 252 will rotate the shaft 234, the rack .2 54 and pinion 255, and the pinions 25!] and 26! which actuate the rack 263 fixed on the slide 230.

The cam slide 245 is actuated in its guideways 245 from the cam drum 82 mounted on the cam drum shaft I! as best seen in Figures II, III, and IV. The shaft 1'! is supported at its outer end in, a suitable bearing 259 in a bracket 21!] appropriately fixed to the left hand end of the base I of th machine by suitable screws 21'! best seen in Figure III. On the tool supporting bars I44 and I45 is slidably mounted the actuating block 212 having a downward depending roller 223 carried on a suitable pin 214 fixed inthe actuating block 212 and which roller 213 operates in an appropriate cam slot formed in the cam drum 82. By this arrangement the block 212 is slid along on the bars I42 and I45 independent of any motion these bars may have. On' one side of the block 212 is provided a pair of lugs, Figure II, forming a slot 215, in which operates a shoe 215 carried in the end of a lever arm 211. The outer end of the bars I 44 and I45 adjacent the blocks H2 is supported by a supplemental bracket 21% carried on the bracket 219 fixed to In this way support is given to the tool bars I44 and I45 for holding th actuating block 212 in proper operative position relative to the cam drum 82. The lever 211 connected through the sleeve 215 to the actuating block 212 is mounted on a pivot pin 229 held in a bifurcated downwardly projecting integral support portion 289 of the overhead rail or tool supporting member 239 and has in its upper end a shoe 28! which operates in an elongated cross slot 282 formed in the cam slide A suitable 246 so that as the cam drum 82 rotates it will slide the actuating block 212 along on the bars M4 and I45 thus rocking the lever 21! and thereby sliding the cam slide 246 in the member 239 to effect feeding of th cutting tool 228 to and from the work piece in the lathe. It is to be further noted that the cam 82 is mounted on the same shaft as the cam drum 8| so that all of the cutting tools including the cutting tool 228 mounted on the tool slid 230 may be operated in a predetermined sequential relationship relative to one another. By appropriately setting the swivel slide 233 around to any desired position the cutting of any steep range of tapers desired with this overhead tool feeding arrangement may be undertaken.

Having fully set forth and described our invention what We claim as new and desire to secure by United States Letters Patent 15:

1. In a lathe having means for receiving and rotating a work piece about a first axis, a bar journaled for rotation on a second axis parallel to said first axis, a tool holder adjustably secured to said bar and adapted to hold a tool in cutting engagement with a work piece in said lathe, plate means guided for translation on said lathe in a direction spaced from and angularly related to said second axis, a form bar adjustably mounted on said plate means, to contact and pivot said holder about th axis of said bar, a cam slide means on said lathe, translatable parallel to said axes, and a connection between said'slid means and plate means, said connection including a cam pivoted on one said means and a pin on the other of said means adapted to coact withsaid cam to variably transmit motion from said slide means to said plate means.

2. In a lathe having a base, a headstock and a tailstcck on said base having centers to receive and rotate a work piece upon a first axis, in combination, a tool bar mounted for pivotal and axial translation in said stocks on a second axis parallel to said first axis, tool holder means adjustably secured to said bar, a plate guided for translation on said base in a direction spaced from, and normal to said second axis, a form bar adjustably fixed to said plate and having a cam edge engaging said holder, a cam slide in said base, adjustable cam connections between said slide and plate, and a single mean having a cam slot therein connected to said bar to efiect translation of said bar and said slide.

WILLIAM F. GROENE. HARRY C. KEMPER. 

